CN103807132A - Swash plate type variable displacement compressor - Google Patents
Swash plate type variable displacement compressor Download PDFInfo
- Publication number
- CN103807132A CN103807132A CN201310524675.1A CN201310524675A CN103807132A CN 103807132 A CN103807132 A CN 103807132A CN 201310524675 A CN201310524675 A CN 201310524675A CN 103807132 A CN103807132 A CN 103807132A
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- Prior art keywords
- swash plate
- chamber
- live axle
- movable body
- axis
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- 238000006073 displacement reaction Methods 0.000 title description 13
- 239000007787 solid Substances 0.000 claims description 28
- 230000033001 locomotion Effects 0.000 claims description 11
- 239000003507 refrigerant Substances 0.000 description 21
- 230000001965 increasing effect Effects 0.000 description 16
- 239000006200 vaporizer Substances 0.000 description 6
- 239000011148 porous material Substances 0.000 description 5
- 210000001061 forehead Anatomy 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002347 injection Methods 0.000 description 2
- 239000007924 injection Substances 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 210000000887 face Anatomy 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1072—Pivot mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
In a compressor, a link mechanism, which allows change of the inclination angle of the swash plate, is arranged between the drive shaft and the swash plate. An actuator is arranged in a swash plate chamber, while being rotational integrally with a drive shaft. The actuator includes a rotation body, a movable body, and a control pressure chamber. The swash plate has a fulcrum, which is coupled to the link mechanism, and a point of application, which is coupled to the movable body. The drive shaft is located between the fulcrum and the point of application.
Description
Technical field
The present invention relates to a kind of ramp type variable compressor.
Background technique
Japanese laid-open patent communique No.5-172052 and No.52-131204 disclose traditional discharge capacity various type tilted-plate compressor (hereinafter, being known as compressor).This compressor comprises suction chamber, discharge chamber, swash plate chamber and is formed on the multiple cylinders hole in housing.Live axle is supported in housing rotatably.The accommodating swash plate in swash plate chamber, swash plate can rotate by the rotation of live axle.The linkage mechanism that allows the tilt angle of swash plate to change is arranged between live axle and swash plate.Tilt angle limits with respect to the line vertical with the spin axis of live axle.Each cylinder pore volume is put the piston of to-and-fro motion mode and is formed thus pressing chamber.Switching mechanism makes each piston to-and-fro motion stroke corresponding with the tilt angle of swash plate in the cylinder hole being associated by the rotation of swash plate.Actuator can change the tilt angle of swash plate and be controlled by control mechanism.
In the compressor of describing in Japanese laid-open patent communique No.5-172052, each cylinder hole is formed in cylinder body, and cylinder body forms the part of housing, and each cylinder hole is formed by the rear cylinder hole that is arranged in the front cylinder hole before swash plate and be arranged in after swash plate.Each piston comprises fore head and occiput, fore head to-and-fro motion in front cylinder hole, occiput and fore head one and to-and-fro motion in rear cylinder hole.
In this compressor, stilling chamber is formed in the rear case member of housing, and except cylinder hole, pilot pressure chamber is formed in cylinder body and with stilling chamber and is communicated with.Pilot pressure chamber is positioned on the homonymy with rear cylinder hole, is positioned at swash plate position below.Actuator arrangement, in pilot pressure chamber, prevents actuator and the rotation of live axle one simultaneously.Particularly, actuator has non-rotating movable body, and the rearward end of non-rotating movable body and live axle is overlapping.The inner peripheral surface of non-rotating movable body is the rearward end of supporting driving shaft rotatably.Non-rotating movable body can move up in the side of the spin axis of live axle.Non-rotating movable body can slide and at the square upward sliding of the spin axis of live axle by its outer circumferential face in pilot pressure chamber.Non-rotating movable body is limited and can not slides around the spin axis of live axle.The Compress Spring that non-rotating movable body is promoted is forward arranged in pilot pressure chamber.Actuator has movable body, and movable body is engaged to swash plate and can moves up in the side of the spin axis of live axle.Thrust bearing is arranged between non-rotating movable body and movable body.The pressure controlled valve that changes the pressure in pilot pressure chamber is arranged between stilling chamber and discharge chamber.By this change of the pressure in pilot pressure chamber, non-rotating movable body and movable body move along spin axis.
Linkage mechanism has movable body and is fixed to the support arm of live axle.Support arm is positioned at a side of swash plate.Movable body has the first elongated hole, and the first elongated hole is extended towards spin axis from the side corresponding to periphery in the direction of the spin axis perpendicular to live axle.Equally, support arm has the second elongated hole, and the second elongated hole is extended towards spin axis from the side corresponding to periphery in the direction of the spin axis perpendicular to live axle.Swash plate has the first arm and the second arm, and the first arm is positioned on rear surface and towards rear cylinder hole and extends, and the second arm is positioned on front surface and towards front cylinder hole and extends.First sells through the first elongated hole so that swash plate and movable body are coupled to each other.The first arm is supported for respect to movable body around the first pin pivotable.Second sells through the second elongated hole so that swash plate and support arm are coupled to each other.The second arm is supported for respect to support arm around the second pin pivotable.The first pin and the second pin extend parallel to each other.By the first pin and the second pin are passed to the first elongated hole and the second elongated hole respectively, the first pin and the second pin are arranged as in swash plate chamber and face with each other, and wherein live axle is between the first pin and the second pin.
In this compressor, when pressure regulator valve is controlled to while opening, allow being communicated with between discharge chamber and stilling chamber, the pressure that this has raise in pilot pressure chamber compared with pressure in swash plate chamber.This advances irrotational movable body and movable body.Therefore, movable body makes the first arm of swash plate around the first pin pivotable, promote swash plate simultaneously.Meanwhile, support arm makes the second arm of swash plate around the second pin pivotable.That is, movable body use first pin position as point of action, swash plate and movable body are coupled to each other in the position of the first pin, and movable body use second sell position as fulcrum, swash plate and support arm are coupled to each other in the position of the second pin, make thus swash plate pivotable.In compressor, thereby the tilt angle of swash plate is increased the stroke that increases each piston, has increased thus the discharge capacity of the every period of rotation of compressor.
On the contrary, close by pilot pressure modulating valve, blocked being communicated with between discharge chamber and stilling chamber.This to the level equating with the stress level in swash plate chamber, makes non-rotating movable body and movable body retreat the pressure decreased in pilot pressure chamber thus.Therefore, compared with the situation increasing with the tilt angle of swash plate, irrotational movable body and movable body move backward.Therefore, movable body makes the first arm of swash plate around the first pin pivotable, pull swash plate simultaneously.Meanwhile, support arm makes the second arm of swash plate around the second pin pivotable.Thus, the tilt angle of swash plate reduces and stroke of piston correspondingly reduces.This has reduced the discharge capacity of the every period of rotation of compressor.
In Japanese laid-open patent communique No.52-131204, in disclosed compressor, actuator is being arranged in swash plate chamber with the mode of live axle one rotation.Particularly, actuator has the solid of rotation rotating with live axle one.The accommodating movable body in inside of solid of rotation, movable body moves up in the side of the spin axis of live axle and can move with respect to solid of rotation.Between solid of rotation and movable body, be formed with pilot pressure chamber, pilot pressure chamber is by being used the pressure in pilot pressure chamber to move movable body.In live axle, be formed with the communicating passage being communicated with pilot pressure chamber.Pressure controlled valve is arranged between communicating passage and discharge chamber.The pressure that pressure controlled valve changes in pilot pressure chamber moves up in the side of spin axis with respect to solid of rotation with permission movable body.The rear end of movable body keeps contacting with hinged ball (hinge ball).Hinged ball is arranged in the central authorities of swash plate and swash plate is attached to live axle to allow swash plate pivotable.Rear end at hinged ball is furnished with Compress Spring, and this Compress Spring pushes hinged ball in the direction at tilt angle that increases swash plate.
Linkage mechanism comprises hinged ball and connecting rod, and linkage arrangement is between solid of rotation and swash plate.Hinged ball contacts with solid of rotation keeping by being positioned at compression springs urges after hinged ball.
First pin vertical with the spin axis of live axle is through the front end of wall.First pin arm and solid of rotation are coupled to each other, and permission arm front end with respect to solid of rotation around the first pin pivotable.Equally, second pin vertical with the spin axis of live axle is through the rear end of arm.Second pin arm and swash plate are coupled to each other, and permission arm rear end with respect to swash plate around the second pin pivotable.In other words, arm and the first pin and the second pin are coupled to each other swash plate and solid of rotation.
In this compressor, in the time that pressure regulator valve control is opened, allow being communicated with between discharge chamber and stilling chamber, the pressure that this has raise in pilot pressure chamber compared with pressure in swash plate chamber.Therefore, movable body retreats and the thrust of resisting Compress Spring promotes hinged ball backward.Meanwhile, arm is around the first pin and the second pin pivotable., the position that compressor use movable body pushes hinged ball is as point of action, and the position that uses swash plate and solid of rotation to be coupled to each other, and---, first pin and second end of selling the arm passing through---, as the strong point, makes swash plate pivotable thus.Therefore,, in the time that the tilt angle of swash plate reduces, stroke of piston reduces.This has reduced the discharge capacity of the every period of rotation of compressor.
On the contrary, close by pilot pressure modulating valve, blocked being communicated with between discharge chamber and stilling chamber.This by the pressure decreased in pilot pressure chamber to the level that equals the stress level in swash plate chamber.Therefore, movable body advances, and the thrust of Compress Spring makes hinged ball follow movable body.This makes swash plate pivotable in the direction of the opposite direction reducing with the tilt angle of swash plate, and tilt angle is increased.Therefore, the stroke of piston increases.
Expect to use the ramp type variable compressor of above-mentioned actuator to there is the higher controllability with regard to displacement control.
In this respect, according to the compressor of describing in Japanese laid-open patent communique No.5-172052, in the time that solid of rotation makes movable body advance on the axial direction at live axle via thrust bearing, thrust bearing may be out of shape.This may cause poor efficiency or power transmission slowly.Therefore, the tilt angle of swash plate may not can change in an advantageous manner, thus, has hindered by optionally increasing and reduce the required displacement control that stroke of piston is carried out.
According to the compressor of describing in Japanese laid-open patent communique No.52-131204, because hinged ball is arranged in the central authorities of swash plate, thereby point of action is positioned near the central authorities of swash plate in the time changing the tilt angle of swash plate.Therefore,, in this compressor, point of action and fulcrum are mutually close.Therefore,, in the time that the movable body of compressor pushes hinged ball, need larger extruding force.The tilt angle that this makes to be difficult to the swash plate that changes in an advantageous manner compressor, hinders required displacement control thus.
Summary of the invention
The object of this invention is to provide the compressor with good displacement control.
In order to realize aforementioned object and according to an aspect of the present invention, ramp type variable compressor is provided, ramp type variable compressor comprises housing, live axle, swash plate, linkage mechanism, piston, switching mechanism, actuator and control mechanism, in described housing, be formed with suction chamber, discharge chamber, swash plate chamber and cylinder hole, described live axle is supported in rotary manner by described housing, and described swash plate can be by rotating in the described swash plate of being rotated in of described live axle chamber.Described linkage mechanism is arranged between described live axle and described swash plate, and allows described swash plate to change with respect to the tilt angle of the line vertical with the spin axis of described live axle.Described piston is received in described cylinder hole in reciprocating mode.Described switching mechanism makes described piston to-and-fro motion stroke corresponding with the described tilt angle of described swash plate in described cylinder hole by the rotation of described swash plate.Described actuator can change the described tilt angle of described swash plate.Actuator described in described control mechanism control.Described actuator arrangement is rotated integratedly in described swash plate chamber and with described live axle.Described actuator comprises solid of rotation, movable body and pilot pressure chamber, described solid of rotation is fixed to described live axle, described movable body is connected to described swash plate and can moves up in the side of the described spin axis of described live axle with respect to described solid of rotation, and described pilot pressure chamber is limited by described solid of rotation and described movable body and utilizes the pressure in described pilot pressure chamber that described movable body is moved.Described control mechanism changes pressure in described pilot pressure chamber so that described movable body moves.Swash plate has fulcrum and point of action, and fulcrum is attached to linkage mechanism, and point of action is attached to movable body.Live axle is between fulcrum and point of action.
According to compressor of the present invention, whole actuator is arranged in swash plate chamber and rotates integratedly with live axle simultaneously.This has eliminated the necessity of the thrust bearing in compressor.Therefore, compressor can change the pressure in pilot pressure chamber effectively and to be rapidly transferred to point of action, makes actuator that high controllability is provided.
In addition, due to fulcrum and point of action be arranged as make live axle in this compressor between fulcrum and point of action, thereby between fulcrum and point of action, produce enough distances.Thus, in the time that the actuator of compressor changes the tilt angle of swash plate, reduced to act on the power on point of action via movable body.In this compressor, the position that swash plate and movable body are coupled to each other is as point of action.This allows the power that is applied to point of action by movable body directly to transfer to swash plate.Therefore, the tilt angle of the swash plate of compressor is easily changed by actuator, and carries out in an advantageous manner displacement control by optionally increasing and reducing stroke of piston.
As implied above, the compressor of present embodiment has good displacement control.
Accompanying drawing explanation
Fig. 1 is the sectional view that the compressor of the first embodiment of the invention in the state corresponding to maximum pump discharge is shown;
Fig. 2 illustrates according to of the present invention first and the schematic diagram of the control mechanism of the compressor of the 3rd mode of execution;
Fig. 3 is the sectional view that the compressor of the first embodiment of the invention in the state corresponding to minimum injection rate is shown;
Fig. 4 illustrates according to of the present invention second and the schematic diagram of the control mechanism of the compressor of the 4th mode of execution;
Fig. 5 be illustrate in the state corresponding to maximum pump discharge according to the sectional view of the compressor of the 3rd mode of execution of the present invention; And
Fig. 6 be illustrate in the state corresponding to minimum injection rate according to the sectional view of the compressor of the 3rd mode of execution of the present invention.
Embodiment
Now with reference to accompanying drawing, first to fourth mode of execution of the present invention is described.The compressor of each in first to fourth mode of execution forms a part for the refrigerating circuit in Vehicular air-conditioning and is arranged in vehicle.
The first mode of execution
As shown in Figure 1 and Figure 3, the compressor of first embodiment of the invention comprises housing 1, live axle 3, swash plate 5, linkage mechanism 7, multiple piston 9, paired front piston shoes 11a and rear piston shoes 11b, actuator 13 and control mechanism 15, and control mechanism 15 is shown in Figure 2.
With reference to Fig. 1, housing 1 there is the rear case member 19 at the front case member 17 of the forward position in compressor, rear positions place in compressor and be arranged in front case member 17 and rear case member 19 between the first cylinder body 21 and the second cylinder body 23.
Swash plate chamber 33 is formed by the first cylinder body 21 and the second cylinder body 23.Swash plate chamber 33 is disposed generally on the middle part of housing 1.
Multiple the first cylinder hole 21a are formed in the first cylinder body 21 and are spaced apart concentrically with equi-angularly space, and extend parallel to each other.The first cylinder body 21 has the first axis hole 21b, and live axle 3 is through the first axis hole 21b.In the first cylinder body 21, be formed with the first recess 21c at the rear position place of the first axis hole 21b.The first recess 21c is communicated with the first axis hole 21b and is coaxial with the first axis hole 21b.The first recess 21c is communicated with swash plate chamber 33.In the inner peripheral surface of the first recess 21c, be formed with step.The first thrust bearing 35a is arranged in the forward position in the first recess 21c.The first cylinder body 21 also comprises the first suction passage 37a, and swash plate chamber 33 and the first suction chamber 27a communicate with each other by the first suction passage 37a.
With the same in the first cylinder body 21, in the second cylinder body 23, be formed with multiple the second cylinder hole 23a.The second axis hole 23b is formed in the second cylinder body 23, and live axle 3 inserts through the second axis hole 23b.The second axis hole 23b is communicated with stilling chamber 31.The second cylinder body 23 has the second recess 23c, and the second recess 23c is positioned at the second axis hole 23b front and is communicated with the second axis hole 23b.The second recess 23c and the second axis hole 23b are coaxially to each other.The second recess 23c is communicated with swash plate chamber 33.In the inner peripheral surface of the second recess 23c, be formed with step.The second thrust bearing 35b is arranged in the rear positions place in the second recess 23c.The second cylinder body 23 also has the second suction passage 37b, and swash plate chamber 33 is communicated with by the second suction passage 37b with the second suction chamber 27b.
Swash plate chamber 33 is connected to unshowned vaporizer by suction port 330, and suction port 330 is formed in the second cylinder body 23.
The first valve plate 39 is arranged between front case member 17 and the first cylinder body 21.The first valve plate 39 has inhalation port 39b and discharges port 39a.The quantity of the quantity of inhalation port 39b and discharge port 39a equals the quantity of the first cylinder hole 21a.Unshowned suction valve arrangement of mechanism is in each inhalation port 39b.Each first cylinder hole 21a is all communicated with the first suction chamber 27a via an inhalation port 39b of correspondence.Unshowned expulsion valve arrangement of mechanism is in each discharge port 39a.Each first cylinder hole 21a is all communicated with the first discharge chamber 29a via a discharge port 39a of correspondence.In the first valve plate 39, be formed with intercommunicating pore 39c.Intercommunicating pore 39c allowed by the first suction passage 37a being communicated with between the first suction chamber 27a and swash plate chamber 33.
The second valve plate 41 is arranged between rear case member 19 and the second cylinder body 23.Similar the first valve plate 39, the second valve plates 41 have inhalation port 41b and discharge port 41a.The quantity of the quantity of inhalation port 41b and discharge port 41a equals the quantity of the second cylinder hole 23a.Unshowned suction valve arrangement of mechanism is in each inhalation port 41b.Each second cylinder hole 23a is all communicated with the second suction chamber 27b via an inhalation port 41b of correspondence.Unshowned expulsion valve arrangement of mechanism is in each discharge port 41a.Each second cylinder hole 23a is all communicated with the second discharge chamber 29b via a discharge port 41a of correspondence.In the second valve plate 41, be formed with intercommunicating pore 41c.Intercommunicating pore 41c allowed by the second suction passage 37b being communicated with between the second suction chamber 27b and swash plate chamber 33.
The first suction chamber 27a and the second suction chamber 27b are communicated with swash plate chamber 33 via the first suction passage 37a and the second suction passage 37b respectively.This makes the pressure in the first suction chamber 27a and the second suction chamber 27b substantially equate with the pressure in swash plate chamber 33.More specifically, the pressure in swash plate chamber 33 is affected by gas blowby and the therefore pressure in each in a little higher than the first suction chamber 27a and the second suction chamber 27b.The refrigerant gas of sending from vaporizer flow to swash plate chamber 33 via suction port 330.Therefore, the pressure in the pressure in swash plate chamber 33 and the first suction chamber 27a and the second suction chamber 27b is lower than the pressure in the first discharge chamber 29a and the second discharge chamber 29b.Therefore, swash plate chamber 33 is low pressure chambers.
Swash plate 5, actuator 13 and flange 3a are attached to live axle 3.Live axle 3 neutralizes in the second axis hole 23b in the second cylinder body 23 through protuberance 17a and the first axis hole 21b of being received in the first cylinder body 21 backward.Thus, the rear end that the front end of live axle 3 is positioned at protuberance 17a and live axle 3 is arranged in stilling chamber 31.Live axle 3 be supported in the mode that can rotate around spin axis O by the wall of the first axis hole 21b in housing 1 and the second axis hole 23b.Swash plate 5, actuator 13 and flange 3a are contained in swash plate chamber 33.Flange 3a is arranged between the first thrust bearing 35a and actuator 13, or more specifically, between the first thrust bearing 35a and movable body 13b, hereinafter will be described.Flange 3a prevents contacting between the first thrust bearing 35a and movable body 13b.Can between the wall of the first axis hole 21b and the second axis hole 23b and live axle 3, adopt radial bearing.
Supporting member 43 is installed around the rear portion of live axle 3 in the mode of extruding.Supporting member 43 has flange 43a and attachment 43b, and flange 43a contacts the second thrust bearing 35b, and the second pin 47b is through attachment 43b, as described below.Axial passage 3b is formed on the rear end from live axle 3 in live axle 3 and in the direction of spin axis O and extends to the front end of live axle 3.Radial passage 3c radially extends and radial passage 3c has opening the outer circumferential face of live axle 3 from the front end of axial passage 3b.Axial passage 3b and radial passage 3c are communicating passage.The rear end of axial passage 3b has the opening in stilling chamber 31, and stilling chamber 31 is low pressure chambers.Radial passage 3c has the opening in the 13c of pilot pressure chamber, hereinafter will be described this.
Swash plate 5 is configured as annular plate and has front surface 5a and rear surface 5b.The front surface 5a of the swash plate 5 in swash plate chamber 33 is towards the front in compressor.The rear surface 5b of the swash plate 5 in swash plate chamber 33 is towards the rear in compressor.Swash plate 5 is fixed to ring flat-plate 45.Ring flat-plate 45 is configured as annular plate and has through hole 45a in centre.By making live axle 3 through through hole 45a, swash plate 5 is attached to live axle 3 and is arranged near the region the second cylinder hole 23a in swash plate chamber 33 with respect to swash plate 5 thus.In other words, swash plate 5 is arranged in the position of more close rear end in swash plate chamber 33.
The far-end of support arm 49 is connected to ring flat-plate 45 by the first pin 47a.Thereby the far-end of this configuration support arm 49 allows the far-end of support arm 49 with respect to ring flat-plate 45 or the axis pivotable around the first pin 47a with respect to swash plate 5 in other words, and the axis of the first pin 47a is the first pivot axis M1.The first pivot axis M1 extends perpendicular to the spin axis O of live axle 3.
The bottom of support arm 49 is connected to supporting member 43 by the second pin 47b.Thereby the bottom of this configuration support arm 49 allows the bottom of support arm 49 with respect to supporting member 43 or the axis pivotable around the second pin 47b with respect to live axle 3 in other words, and the axis of the second pin 47b is the second pivot axis M2.The second pivot axis M2 is parallel to the first pivot axis M1 and extends.Support arm 49 and the first pin 47a and the second pin 47b are equivalent to according to linkage mechanism 7 of the present invention.
In compressor, allow swash plate 5 to pass through the connection between swash plate 5 and live axle 3 via linkage mechanism 7 and rotation together with live axle 3.The end of support arm 49 can be respectively around the first pivot axis M1 and the second pivot axis M2 pivotable.Therefore,, in the time that swash plate 5 changes with respect to the tilt angle of the spin axis O of live axle 3, allow swash plate 5 to use the first pin 47a(, the first pivot axis M1) as the fulcrum of pivot movement, swash plate 5 is connected to one end of ring flat-plate 45 at the first pin 47a place.For purpose of explanation, fulcrum refers to the point on the first pivot axis.The first pivot axis and fulcrum are represented by same reference numerals M1.
Piston 9 is included in the first piston head 9a at front end place and the second piston head 9b in rear end separately.First piston head 9a is received in the first corresponding cylinder hole 21a in reciprocating mode and forms the first pressing chamber 21d.The second piston head 9b is contained in the second corresponding cylinder hole 23a in reciprocating mode and forms the second pressing chamber 23d.Each piston 9 has recess 9c.The accommodating semicircular piston shoes 11a of each recess 9c, 11b.Piston shoes 11a, 11b convert the rotation of swash plate 5 to the to-and-fro motion of piston 9.Piston shoes 11a, 11b are equivalent to according to switching mechanism of the present invention.Thus, first piston head 9a and the first cylinder hole 21a and in second cylinder hole 23a to-and-fro motion with the tilt angle of swash plate 5 corresponding stroke of the second piston head 9b in correspondence.
Ring flat-plate 45 is connected to the attachment 130c of movable body 13b by the 3rd pin 47c.In this way, ring flat-plate 45 or in other words swash plate 5 are supported to and are made to allow ring flat-plate 45 or swash plate 5 around the 3rd pin 47c pivotable by movable body 13b, and the 3rd pin 47c is operative axis M3.Operative axis M3 is parallel to the first pivot axis M1 and the second pivot axis M2 extends.The first pivot axis M1 and operative axis M3 lay respectively at the top and bottom of ring flat-plate 45, and wherein, through hole 45a---is live axle 3---between the top and bottom of ring flat-plate 45., live axle 3 is between fulcrum M1 and point of action M3.Therefore, movable body 13b remains under the state that is connected to swash plate 5.In the time of the maximum of the tilt angle of swash plate 5, movable body 13b contacts with flange 3a.Therefore,, in compressor, movable body 13b can remain on allowable angle of inclination place by swash plate 5.Swash plate 5 can by with the 3rd pin 47c or operative axis M3 as point of action M3 and by change the tilt angle of swash plate 5 as fulcrum M1 with the first pivot axis M1, swash plate 5 and attachment 130c sell 47c or operative axis M3 place interconnects the 3rd.For purpose of explanation, operative axis and point of action M3 are represented by same reference numerals M3.
Between solid of rotation 13a and movable body 13b, be limited with pilot pressure chamber 13c.Radial passage 3c has the opening in the 13c of pilot pressure chamber.Pilot pressure chamber 13c is communicated with stilling chamber 31 by radial passage 3c and axial passage 3b.
With reference to Fig. 2, control mechanism 15 comprises leakage path 15a and supply passage 15b, control valve 15c and throttle orifice 15d, and leakage path 15a and supply passage 15b are each as control channel.
Be formed with screw section 3d at the far-end of live axle 3.Live axle 3 is connected to the belt wheel of unshowned belt wheel and unshowned magnetic clutch by screw section 3d.The unshowned band being driven by vehicle motor is wound around around the belt wheel of belt wheel or magnetic clutch.
The pipeline (not shown) extending to vaporizer is connected to suction port 330.The pipeline extending to condenser (also not shown) is connected to exhaust port.Compressor, vaporizer, expansion valve and condenser form the refrigerating circuit in Vehicular air-conditioning.
In the compressor with above-mentioned structure, live axle 3 rotates so that swash plate 5 rotates, and therefore makes piston 9 to-and-fro motion in the first corresponding cylinder hole 21a and the second cylinder hole 23a.This has changed the volume of the each first pressing chamber 21d corresponding with stroke of piston and the volume of each the second pressing chamber 23d.Thus, refrigerant gas via suction port 330 from vaporizer be drawn into swash plate chamber 33 and be sent to the first suction chamber 27a and the second suction chamber 27b in.Then, refrigerant gas compressed before being sent in the first discharge chamber 29a and the second discharge chamber 29b in the first pressing chamber 21d and the second pressing chamber 23d.Then, refrigerant gas passes out to condenser from the first discharge chamber 29a and the second discharge chamber 29b by exhaust port.
Meanwhile, rotating member---comprises swash plate 5, ring flat-plate 45, support arm 49 and the first pin 47a---and is subject to the centrifugal force acting in the direction that the tilt angle of swash plate 5 is reduced.This variation at the tilt angle by swash plate 5, carries out displacement control by the stroke optionally increasing and reduce each piston 9.
Particularly, in control mechanism 15, in the time that the control valve 15c shown in Fig. 2 reduces to flow to the amount of the refrigerant gas in supply passage 15b, the amount that flow to the refrigerant gas the second suction chamber 27b by leakage path 15a from stilling chamber 31 increases.This makes the pressure in pressure and the second suction chamber 27b in the 13c of pilot pressure chamber roughly equal.Therefore, in the time acting on centrifugal force on rotating member movable body 13b moved backward, pilot pressure chamber 13c reduce dimensionally and thus the tilt angle of swash plate 5 reduce.
; with reference to Fig. 3; when the pressure drop in the 13c of pilot pressure chamber and thus the pressure difference between pilot pressure chamber 13c and swash plate chamber 33 decline time, the centrifugal force acting on rotating member moves movable body 13b in swash plate chamber 33 on the axial direction of live axle 3.Therefore, in swash plate chamber 33, at point of action M3,---it is operative axis M3---located, and movable body 13b promotes the bottom of ring flat-plate 45, the i.e. bottom of swash plate 5 backward via attachment 130c.This makes the bottom of swash plate 5 around the counterclockwise pivotable of operative axis M3.In addition, the far-end of support arm 49 is around the clockwise pivotable of the first pivot axis M1, and the bottom of support arm 49 is around the clockwise pivotable of the second pivot axis M2.Thus, support arm 49 approaches the flange 43a of supporting member 43.Thus, swash plate 5 is arranged in the first pivot axis M1 that the operative axis M3 at rear portion is arranged in top as point of action M3 with by use as fulcrum M1 pivotable by use.Therefore, reduce the tilt angle of swash plate 5 by the spin axis O with respect to live axle 3, reduce thus the stroke of each piston 9, the intake of every period of rotation compressor and discharge capacity decline.The tilt angle of the swash plate 5 shown in Fig. 3 is corresponding to the minimal tilt angle of compressor.
The swash plate 5 of compressor is subject to acting on the centrifugal force on counterweight part 49a.Easily move up in the side that reduces tilt angle thus.Movable body 13b moves backward on the axial direction of live axle 3 and the rear end of movable body 13b is arranged in the inner side of counterweight part 49a.Therefore,, in the time that the tilt angle of the swash plate 5 of compressor reduces, the approximately half of the rear end of counterweight part 49a and movable body 13b is overlapping.
If the control valve 15c shown in Fig. 2 has increased the amount that flow to the refrigerant gas in supply passage 15b, so, contrary with the situation that reduces compressor displacement, the amount that flow to the refrigerant gas stilling chamber 31 from the second discharge chamber 29b by supply passage 15b increases.Therefore, the pressure in pilot pressure chamber equates substantially with the pressure in the second discharge chamber 29b.This makes the movable body 13b of actuator 13 overcome the centrifugal force acting on rotating member to move forward.This has increased the volume of pilot pressure chamber 13c and the tilt angle that has increased swash plate 5.
,, with reference to Fig. 1, because the pressure in the 13c of pilot pressure chamber exceedes the pressure in swash plate chamber 33, thereby movable body 13b moves forward in swash plate chamber 33 along the axial direction of live axle 3.Thus, movable body 13b pulls the bottom of swash plate 5 by the attachment 130c at operative axis M3 place to 33Zhong forward position, swash plate chamber.This makes the bottom of swash plate 5 around the clockwise pivotable of operative axis M3.In addition, the far-end of support arm 49 around the bottom of the counterclockwise pivotable of the first pivot axis M1 and support arm 49 around the counterclockwise pivotable of the second pivot axis M2.Thus, support arm 49 separates with the flange 43a of supporting member 43.This makes pivotable in the direction of the opposite direction of swash plate 5 in the situation reducing with tilt angle, and wherein operative axis M3 and the first pivot axis M1 are used separately as point of action M3 and fulcrum M1.Therefore, swash plate 5 increases with respect to the tilt angle of the spin axis O of live axle 3.This has increased the stroke of each piston 9, has increased thus intake and the discharge capacity of the every period of rotation of compressor.The tilt angle of the swash plate 5 shown in Fig. 1 is corresponding to the allowable angle of inclination in compressor.
In this compressor, the 3rd pin 47c that has the first pin 47a of the first pivot axis M1 and have an operative axis M3 lays respectively at the top and bottom place of ring flat-plate 45.Therefore, swash plate 5 has fulcrum M1 and the point of action M3 in the time changing the tilt angle of swash plate 5 at operative axis M3 and the first residing position of pivot axis M1.Operative axis M3 and the first pivot axis M1 are positioned on swash plate 5, and wherein live axle 3 is between operative axis M3 and the first pivot axis M1., live axle 3 swash plate 5 in the radial direction between operative axis M3 and the first pivot axis M1.Therefore, between operative axis M3 and the first pivot axis M1, produce enough distances.Thus, in the time that the actuator 13 of compressor changes the tilt angle of swash plate 5, can reduce to act on motive force and the extruding force on operative axis M3 via movable body 13b.In this compressor, swash plate 5 is used as point of action M3 with the position that movable body 13b is coupled to each other.This allows the motive force and the extruding force that are applied to operative axis M3 by movable body 13b directly to transfer to swash plate 5.
In addition, in this compressor, the first pivotal axis M1 and operative axis M3 are not only parallel to each other but also the first pivotal axis M1 is also parallel with the second pivot axis M2 with operative axis M3.Thus, in the time that the tilt angle of the swash plate 5 of compressor changes, the motive force and the extruding force that are applied to operative axis M3 via movable body 13b allow easily pivotable of linkage mechanism 7.
In addition,, in this compressor, support arm 49, the first pin 47a and the second pin 47b form linkage mechanism.In addition, in this compressor, swash plate 5 passes through the far-end of the first pin 47a support arm 49 to allow the far-end of support arm 49 around the first pivot axis M1 pivotable.Live axle 3 passes through the bottom of the second pin 47b support arm 49 to allow the bottom of support arm 49 around the second pivot axis M2 pivotable.
Therefore, the structure of the simplification of linkage mechanism 7 has reduced the size of linkage mechanism 7, has also reduced the size of compressor.Swash plate 5 is supported on the operative axis M3 of attachment 130c of movable body 13b pivotally.Be applied to the motive force of operative axis M3 and the tilt angle of extruding force change swash plate 5 by the movable body 13b of compressor, make swash plate 5 rotate around operative axis M3 simultaneously.Therefore, can increase the change amount at the tilt angle of swash plate 5, reduce to be applied to motive force and the extruding force of spin axis M3 simultaneously.
Therefore,, except acting on the centrifugal force on rotating member, the centrifugal force acting on counterweight part 49a plays the effect at the tilt angle that reduces swash plate 5.This allows swash plate 5 pivotable easily in the direction that reduces tilt angle.Therefore,, in the time reducing the tilt angle of swash plate 5 of compressor, can reduce to be applied to by movable body 13b the extruding force of operative axis M3.In addition, counterweight part 49a extends accordingly with this circumference of about half on the circumferencial direction of actuator 13, in the time that movable body 13b moves backward on the axial direction of live axle 3, and the rearward end of the about half of counterweight part 49a and movable body 13b overlapping (with reference to Fig. 3).Thus, the existence of counterweight part 49a does not limit the movably scope of movable body 13b.
Therefore, the tilt angle of the swash plate 5 of compressor is easily changed by actuator 13, and carries out in an advantageous manner displacement control by optionally increasing and reducing stroke of piston.
In addition, in this compressor, whole actuator 13 is arranged in swash plate chamber 33, while and live axle 3 one.This has eliminated the necessity of the thrust bearing in compressor.Therefore, compressor can change the pressure in the 13c of pilot pressure chamber effectively and rapidly to transfer to point of action M3, makes actuator 13 bring into play high controllability.
As implied above, the compressor of the first mode of execution has controllability good with regard to displacement control.
Ring flat-plate 45 is attached to swash plate 5 and supporting member 43 is installed around live axle 3.This structure is guaranteed the easy assembling in compressor between swash plate 5 and support arm 49 and between live axle 3 and support arm 49.In addition, in this compressor, by live axle 3 is easily rotatably arranged swash plate 5 through the through hole 45a of ring flat-plate 45 around live axle 3.
In addition, in the control mechanism 15 of compressor, leakage path 15a allows being communicated with between pilot pressure chamber 13c and the second suction chamber 27b.Supply passage 15b allows being communicated with between pilot pressure chamber 13c and the second discharge chamber 29b.Control valve 15c regulates the aperture of supply passage 15b.Therefore, compressor, by using the pressure in the high-voltage high-speed ground rising pilot pressure chamber 13c in the second discharge chamber 29b, has promptly increased compressor displacement thus.
In addition, the swash plate chamber 33 of compressor is used as the path of refrigerant gas to the first suction chamber 27a and the second suction chamber 27b.This has produced baffler effect.Therefore, the suction pulsation of refrigerant gas reduces, thus the noise that has reduced to be produced by compressor.
The second mode of execution
Compressor second embodiment of the invention comprises the control mechanism 16 shown in Fig. 4, and it has substituted the control mechanism 15 of the compressor of the first mode of execution.Control mechanism 16 comprises leakage path 16a and supply passage 16b, control valve 16c and throttle orifice 16d, and leakage path 16a and supply passage 16b are each as control channel.
In the control mechanism 16 of this compressor, if control valve 16c reduces the amount of refrigerant gas mobile in leakage path 16a, so, from the second discharge chamber 29b mobile enhancing to the refrigerant gas stilling chamber 31 via supply passage 16b and throttle orifice 16d.This makes the pressure in the 13c of pilot pressure chamber be substantially equal to the pressure in the second discharge chamber 29b.The centrifugal force of this movable body 13b resistant function that makes actuator 13 on rotating member moves forward.This has increased the volume of pilot pressure chamber 13c the tilt angle that has increased swash plate 5.
In the compressor of the second mode of execution, as according in the situation (see figure 1) of the compressor of the first mode of execution, the tilt angle of swash plate 5 increases the stroke of each piston 9, makes thus the intake of the every period of rotation of compressor and discharge capacity raise.
On the contrary, if the control valve 16c shown in Fig. 4 increases the amount of refrigerant gas mobile in leakage path 16a, so, unlikely flow in stilling chamber 31 and be stored in stilling chamber 31 by supply passage 16b and throttle orifice 16d from the refrigerant gas of the second discharge chamber 29b.This makes the pressure in the 13c of pilot pressure chamber be substantially equal to the pressure in the second suction chamber 27b.Thus, by the centrifugal force acting on solid of rotation, movable body 13b is moved backward.The volume that this has reduced pilot pressure chamber 13c, has reduced the tilt angle of swash plate 5 thus.
Therefore,, by reducing the tilt angle of swash plate 5 and reducing thus the stroke of each piston 9, reduced intake and the discharge capacity (see figure 3) of the every period of rotation of compressor.
Just as already described, the control mechanism 16 of the compressor of the second mode of execution regulates the aperture of leakage path 16a by control valve 16c.Thus, thus the pressure that compressor reduces in the 13c of pilot pressure chamber lentamente by the low pressure using in the second suction chamber 27a keeps required vehicle drive travelling comfort.Other operation of the compressor of the second mode of execution is identical with the respective operations of the compressor of the first mode of execution.
The 3rd mode of execution
As shown in Figures 5 and 6, comprise housing 10 and piston 90 according to the compressor of the 3rd mode of execution of the present invention, it substitutes housing 1 and the piston 9 of the compressor of the first mode of execution.
Except rear case member 19 and the second cylinder body 23, housing 10 also has front case member 18, and wherein rear case member 19 is parts identical with the parts of the first mode of execution with the second cylinder body 23.Front case member 18 has recess 18b and outstanding protuberance 18a forward.Shaft sealer 25 is arranged in protuberance 18a.Unlike the front case member 17 of the first mode of execution, front case member 18 neither comprises that the first suction chamber 27a does not comprise the first discharge chamber 29a yet.
In this compressor, swash plate chamber 33 is formed by front case member 18 and the second cylinder body 23.Swash plate chamber 33 is substantially arranged in the middle part of housing 10 and is communicated with the second suction chamber 27b via the second suction passage 37b.The first thrust bearing 35a is arranged in the recess 18b of front case member 18.
Unlike the piston 9 of the first mode of execution, each piston 90 only has the piston head 9b in the rear end of piston 90.Other parts of each piston 90 of the 3rd mode of execution and other parts of compressor are configured to identical with the corresponding component of the first mode of execution.For purpose of explanation, in the following description about the 3rd mode of execution, the second cylinder hole 23a, the second pressing chamber 23d, the second suction chamber 27b and the second discharge chamber 29b of the first mode of execution will be called as cylinder hole 23a, pressing chamber 23d, suction chamber 27b and discharge chamber 29b.
In the compressor of the 3rd mode of execution, thereby live axle 3 rotates swash plate 5 is rotated, and makes thus piston 90 to-and-fro motion in corresponding cylinder hole 23a.Thus, the volume of each pressing chamber 23d and stroke of piston change accordingly.Correspondingly, refrigerant gas is drawn into swash plate chamber 33, arrives each pressing chamber 23d to compress, to be sent in discharge chamber 29b again by suction chamber 27b from vaporizer by suction port 330.Then, refrigerant gas is supplied to condenser by unshowned exhaust port from discharge chamber 29b.
The compressor of similar the first mode of execution, the compressor of the 3rd mode of execution can optionally increase and reduce by changing the tilt angle of swash plate 5 stroke of each piston 90, thereby carries out displacement control.
As shown in Figure 6, the centrifugal force that in the time that the pressure difference between pilot pressure chamber 13c and swash plate chamber 33 reduces, acts on rotating member on---comprising swash plate 5, ring flat-plate 45, support arm 49 and the first pin 47a---moves movable body 13b in swash plate chamber 33 on the axial direction of live axle 3.Therefore, movable body 13b promotes backward the bottom of swash plate 5 in swash plate chamber 33.This makes swash plate 5 pivotables, and wherein operative axis M3 is used as fulcrum M1 as point of action M3 and the first pivot axis M1, as the situation of the first mode of execution.Therefore, the tilt angle of swash plate 5 is reduced to the stroke of piston 90 is reduced, and the intake of the every period of rotation of compressor and discharge capacity reduce.The tilt angle of the swash plate 5 shown in Fig. 6 is corresponding to the minimal tilt angle in compressor.
With reference to Fig. 5, because the pressure in the 13c of pilot pressure chamber exceedes the pressure in swash plate chamber 33, thereby the centrifugal force of movable body 13b resistant function on rotating member and moving forward on the axial direction of live axle 3 in swash plate chamber 33.Therefore, movable body 13b pulls forward the bottom of swash plate 5 in swash plate chamber 33.This makes pivotable in the direction of the opposite direction of swash plate 5 in the situation reducing with tilt angle, and wherein operative axis M3 and the first pivot axis M1 are used separately as point of action M3 and fulcrum M1.Therefore, the tilt angle of swash plate 5 increases the stroke increase that makes piston 90, and the intake of the every period of rotation of compressor and discharge capacity increase.The tilt angle of the swash plate 5 shown in Fig. 5 is corresponding to the allowable angle of inclination in compressor.
The compressor of the 3rd mode of execution is not formed with the first cylinder body 21 and has simple structure thus compared with the compressor of the first mode of execution.Therefore, the compressor of the 3rd mode of execution further reduces dimensionally.Other operation of the 3rd mode of execution is identical with the respective operations of the first mode of execution.The 4th mode of execution
According to the compressor of the 4th mode of execution of the present invention be use the control mechanism 16 shown in Fig. 4 according to the compressor of the 3rd mode of execution.The compressor of the 4th mode of execution operates in the mode identical with the compressor of the second mode of execution and the 3rd mode of execution.
Although with reference to the first mode of execution to the four mode of executions, invention has been described, the mode of execution that the invention is not restricted to illustrate, but can retrofit without departing from the scope of the invention as required.
For example, in the compressor of the first mode of execution to the four mode of executions, refrigerant gas is sent in the first suction chamber 27a and the second suction chamber 27b via swash plate chamber 33.But refrigerant gas can directly be inhaled into the first suction chamber 27a and the second suction chamber 27b by suction port from corresponding pipeline.In this case, compressor should be configured to allow being communicated with between the first suction chamber 27a and the second suction chamber 27b and swash plate chamber 33 to make swash plate chamber 33 be equivalent to low pressure chamber.
The compressor of the first mode of execution to the four mode of executions can be configured to there is no stilling chamber 31.
Claims (6)
1. a ramp type variable compressor, described ramp type variable compressor comprises:
Housing (1) is formed with suction chamber (27a, 27b), discharge chamber (29a, 29b), swash plate chamber (33) and cylinder hole (21a, 23a) in described housing (1);
Live axle (3), described live axle (3) is supported in rotary manner by described housing (1);
Swash plate (5), described swash plate (5) can be by the rotation in described swash plate chamber (33) that is rotated in of described live axle (3);
Linkage mechanism (7), described linkage mechanism (7) is arranged between described live axle (3) and described swash plate (5), and described linkage mechanism allows described swash plate (5) to change with respect to the tilt angle of the line vertical with the spin axis of described live axle (3);
Piston (9), described piston (9) is received in described cylinder hole (21a, 23a) in reciprocating mode;
Switching mechanism (11a, 11b), described switching mechanism (11a, 11b) makes described piston (9) to-and-fro motion stroke corresponding with the described tilt angle of described swash plate (5) in described cylinder hole (21a, 23a) by the rotation of described swash plate (5);
Actuator (13), described actuator (13) can change the described tilt angle of described swash plate (5); And
Control mechanism (15,16), described control mechanism (15,16) is controlled described actuator (13),
Described ramp type variable compressor is characterised in that,
Described actuator (13) is arranged in described swash plate chamber (33) and with described live axle (3) and rotates integratedly,
Described actuator (13) comprises solid of rotation (13a), movable body (13b) and pilot pressure chamber (13c), described solid of rotation (13a) is fixed to described live axle (3), described movable body (13b) is connected to described swash plate (5) and can moves up in the side of the described spin axis of described live axle (3) with respect to described solid of rotation (13a), described pilot pressure chamber (13c) is limited by described solid of rotation (13a) and described movable body (13b) and utilizes the pressure in described pilot pressure chamber (13c) to make described movable body (13b) mobile
Described control mechanism (15,16) changes the pressure in described pilot pressure chamber (13c) so that described movable body (13b) is mobile, and
Described swash plate (5) has fulcrum (M1) and point of action (M3), and described fulcrum (M1) is attached to described linkage mechanism (7), and described point of action (M3) is attached to described movable body (13b), and
Described live axle (3) is positioned between described fulcrum (M1) and described point of action (M3).
2. ramp type variable compressor according to claim 1, wherein,
Described fulcrum (M1) is the point being positioned on the first pivot axis (M1), described the first pivot axis ground supports described linkage mechanism (7), wherein said the first pivot axis (M1) is perpendicular to the described spin axis (O) of described live axle (3), and
Described point of action (M3) is the point being positioned in operative axis (M3), and described operative axis (M3) can be slidably supported movable body (13b), and wherein said operative axis (M3) is parallel with described the first pivot axis (M1).
3. ramp type variable compressor according to claim 2, wherein,
Described linkage mechanism (7) has support arm (49),
Described support arm (49) has far-end and bottom, described far-end is supported to and is allowed described far-end around the first pivot axis (M1) pivotable by described swash plate (5), described the first pivot axis (M1) is perpendicular to described spin axis (O), described bottom is supported to and is allowed described bottom around the second pivot axis (M2) pivotable by described live axle (3), described the second pivot axis (M2) is parallel to described the first pivot axis (M1), and
Described swash plate (5) is supported to and is made to allow described swash plate (5) around operative axis (M3) pivotable by described movable body (13b), and described operative axis (M3) is parallel to described the first pivot axis (M1) and described the second pivot axis (M2).
4. ramp type variable compressor according to claim 3, wherein,
Described support arm (49) comprises counterweight part (49a), and described counterweight part (49a) extends in a side contrary with described the second pivot axis (M2) with respect to described the first pivot axis (M1), and
Described counterweight part (49a) rotates described swash plate (5) is applied to reduce the power at described tilt angle around described spin axis (O).
5. according to the ramp type variable compressor described in claim 3 or 4, wherein,
Described swash plate (5) has the first member (45), described the first member (45) supports the described far-end of described support arm (49) to allow the described far-end of described support arm (49) around described the first pivot axis (M1) pivotable, and described the first member (45) can be around described operative axis (M3) pivotable, and
Described the first member (45) has through hole (45a), and described live axle (3) is through described through hole (45a).
6. ramp type variable compressor according to claim 5, wherein, second component (43) is fixed to described live axle (3), and the described bottom that described second component (43) supports described support arm (49) is to allow the described bottom of described support arm (49) around described the second pivot axis (M2) pivotable.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012243988A JP6028525B2 (en) | 2012-11-05 | 2012-11-05 | Variable capacity swash plate compressor |
| JP2012-243988 | 2012-11-05 |
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| CN103807132A true CN103807132A (en) | 2014-05-21 |
| CN103807132B CN103807132B (en) | 2016-08-17 |
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| US (1) | US9228577B2 (en) |
| EP (1) | EP2728182A3 (en) |
| JP (1) | JP6028525B2 (en) |
| KR (1) | KR101486662B1 (en) |
| CN (1) | CN103807132B (en) |
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| CN104755759B (en) | 2012-11-05 | 2016-12-07 | 株式会社丰田自动织机 | Variable displacement swash plate compressor |
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| JP2016102419A (en) * | 2014-11-27 | 2016-06-02 | 株式会社豊田自動織機 | Variable displacement swash plate compressor |
| JP2016151188A (en) * | 2015-02-16 | 2016-08-22 | 株式会社豊田自動織機 | Variable displacement swash plate compressor |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104074712A (en) * | 2013-03-29 | 2014-10-01 | 株式会社丰田自动织机 | Variable displacement swash plate type compressor |
| CN105074209A (en) * | 2013-03-29 | 2015-11-18 | 株式会社丰田自动织机 | Variable displacement swash-plate compressor |
| US9523357B2 (en) | 2013-03-29 | 2016-12-20 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate type compressor |
| CN104074712B (en) * | 2013-03-29 | 2017-04-12 | 株式会社丰田自动织机 | Variable displacement swash plate type compressor |
| CN104948419A (en) * | 2014-03-28 | 2015-09-30 | 株式会社丰田自动织机 | Variable displacement swash plate compressor |
| CN104948419B (en) * | 2014-03-28 | 2017-06-27 | 株式会社丰田自动织机 | Variable displacement rotary slope plate type compressor |
| US9709045B2 (en) | 2014-03-28 | 2017-07-18 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
| US9790936B2 (en) | 2014-03-28 | 2017-10-17 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
| US9803629B2 (en) | 2014-03-28 | 2017-10-31 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
| US9903353B2 (en) | 2014-03-28 | 2018-02-27 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
| US9903354B2 (en) | 2014-03-28 | 2018-02-27 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor |
| US9915252B2 (en) | 2014-03-28 | 2018-03-13 | Kabushiki Kaisha Toyota Jidoshokki | Variable displacement swash plate compressor having a fulcrum and an action point located on opposite sides of a drive shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2728182A3 (en) | 2017-03-01 |
| US20140127042A1 (en) | 2014-05-08 |
| BR102013028050A2 (en) | 2014-10-21 |
| CN103807132B (en) | 2016-08-17 |
| EP2728182A2 (en) | 2014-05-07 |
| JP2014092107A (en) | 2014-05-19 |
| US9228577B2 (en) | 2016-01-05 |
| JP6028525B2 (en) | 2016-11-16 |
| KR20140058341A (en) | 2014-05-14 |
| KR101486662B1 (en) | 2015-01-26 |
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